US4106883A - Distributing valve on a hydraulic rotary piston engine - Google Patents

Distributing valve on a hydraulic rotary piston engine Download PDF

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Publication number
US4106883A
US4106883A US05/771,979 US77197977A US4106883A US 4106883 A US4106883 A US 4106883A US 77197977 A US77197977 A US 77197977A US 4106883 A US4106883 A US 4106883A
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US
United States
Prior art keywords
ports
valve members
gear
rotatable
port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/771,979
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English (en)
Inventor
Gunnar Lyshoj Hansen
Leif Viggo Sturlason
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Danfoss AS
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Danfoss AS
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Publication date
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Publication of US4106883A publication Critical patent/US4106883A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves
    • F04C2/106—Spool type distribution valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86638—Rotary valve
    • Y10T137/86646—Plug type
    • Y10T137/86662—Axial and radial flow

Definitions

  • the invention relates to a distributing valve on a hydraulic rotary piston engine comprising an externally serrated gear member (gear) and an internally serrated gear member (gear ring) which surrounds same, has one additional tooth and forms displacement cells therewith, wherein two valve members, one fixed to each gear member, co-operate with one another in the manner of a rotary slide along a surface of the cylinder and are there provided with axially extending control orifices which substantially avoid impacts, the control orifices of one valve member each lead by way of a passage to one displacement cell and their number corresponds to the number of teeth of the gear member secured thereto, and the control orifices of the other valve member are connected in alternate sequence to the engine inlet and outlet and their number corresponds to twice the number of teeth of the gear member secured thereto.
  • each second longitudinal web between the control orifices is only locally provided with circumferentially diverging bridging incisions of small orifice cross-section and preferably converging in triangular formation.
  • the bridging incisions reduce this sudden opening pulse because the pressure build-up already begins when the bridging incision comes to lie under the opposite orifice.
  • triangular orifices one can achieve a practically smooth gradual transition instead of a steep pressure rise flank.
  • the invention is based on the problem of providing a distributing valve of the aforementioned kind in which no additional machining is necessary in order substantially to avoid the pressure pulses.
  • control orifices of the one valve member extend at a small angle obliquely to the parallel axis.
  • an angle that is too small because otherwise the differences from sudden opening would hardly be noticeable.
  • the angle must not be too large because otherwise difficulties may arise during covering by means of the sealing webs remaining between the other control orifices.
  • An angle that is particularly suitable in practice is about 3° to 8°.
  • control orifices can be selectively applied to the one or other valve member, irrespective of whether one is concerned with the internal or external periphery. Simplification of the work is sometimes obtained if the control orifices connected to the displacement cells extend obliquely because this is the lesser amount.
  • control orifices collected to the displacement cells can be covered substantially accurately by every second of the sealing webs remaining between the other control orifices but more than amply covered by the intermediate sealing webs.
  • the displacement cell having the largest volume is momentarily completely closed during pressure change. The pressure created therein relieves the two adjacent teeth. The build-up and reduction of pressure presents no difficulties because of the gradual transition.
  • FIG. 1 is a longitudinal section through a rotary piston engine
  • FIG. 2 is a plan view of the rotary slide
  • FIGS. 3A and 3B show a development of the rotary slide with the associated position of the gear elements
  • FIGS. 4A and 4B show a similar representation as in FIGS. 3A and 3B but in a different operating position
  • FIG. 5 is a development of a modified embodiment.
  • a housing 1 carries at one side a cover 3 secured by screws 2 and at the other side an intermediate plate 5 likewise secured by screws 4, an internally serrated gear ring 6 and a cover 7.
  • a Cardan shaft 13 for balancing out the gyratory movement of the centre of gravity is connected to the gear, its other end engaging in a valve member 14 in the form of a rotary slide which is in one piece with the main shaft 12 and which, along a surface of the cylinder, co-operates with a second valve member 15 formed by the bore of the housing 1.
  • Two circumferential grooves 16 and 17 are provided in the rotary slide.
  • the circumferential groove 16 constantly communicates with the inlet opening 8 and the circumferential groove 17 constantly communicates with the outlet opening.
  • control orifices 18 in the form of grooves communicating with the circumferential groove 16 and control orifices 19 in the form of grooves communicating with the circumferential groove 17.
  • the number of control orifices 18 and 19 in each case corresponds to the number of teeth of the gear 11.
  • control orifices 20 in the form of apertures which are connected by passages 21 to the displacement cells 22 formed between the teeth of the gear and gear ring. Accordingly, the displacement cells 22 are alternately connected to the inlet 9 and the outlet 10 so that continual rotating will result in the case of a motor.
  • the engine works as a pump.
  • control orifices 20 extend in a direction parallel to the axis.
  • the control orifices 18 and 19, however, are oblique to this parallel axis by an angle ⁇ . This is particularly evident from the FIG. 2 plan view of the valve member 14.
  • the angle ⁇ in this case amounts to about 5°.
  • control orifices 18 and 19 are of the same size and the control orifices 20 are also all of the same size
  • a narrower sealing web 23 and a broader sealing web 24 alternately follow one another between the control orifices on the valve member 14.
  • the narrower sealing web 23 is dimensioned for obliquity and width so that it can substantially accurately cover one control orifice 20 as is shown in the middle of FIG. 4.
  • the sealing web 24, on the other hand, is dimensioned so that it more than covers the control orifice 20, as shown in the middle of FIG. 3.
  • the representation of FIGS. 3 and 4 assume that seven displacement chambers 22 are provided which are bonded by a gear ring 6 having seven teeth and a gear 11 with six teeth.
  • the obliquity of the control orifices 18 and 19 ensures that when overcontrolling the control orifices 20 their entire side edge 25 is not released all at once but such release extends along a path depending on the obliquity. The same applies when closing this control orifice. Consequently, before and after the actual opening a transition cross-section is available which, because of its small size, has a throttling effect and therefore does not yet initiate an engine function but permits a pressure build-up or reduction in the displacement cells 22 and the associated passages 21. Pressure pulses are avoided in this way.
  • the larger width of the sealing web 24 has the result that, as shown in FIG. 3, the largest displacement cell 22 max at any one time is excessively covered (26) so that this cell is momentarily covered, namely substantially during its reduction phase because of the rotary play between the gear 11 and valve member 14.
  • a build-up in this cell as a result of a change in volume leads to a relief of the tooth crests.
  • This pressure build-up does not detrimentally affect operation because the pressure peak is gradually reduced during the subsequent release of the control orifice 25. As is desired, this effect of occurs only during a pressure change of the largest diplacement cell 22 max but not during a pressure change of the smallest displacement cell 22 min as is shown in FIG. 4.
  • FIG. 5 illustrates a modification in which corresponding parts are referred to by reference numberals that are increased by 100.
  • the valve member 114 has control orifices 118 and 119 parallel to the axis whilst the control orifices 120 in the valve member at the side of the housing are oblique. It will be seen that similar effects are achievable in this case.
  • control orifices can be produced in the conventional manner.
  • Oblique grooves can be simply produced by positioning a milling cutter plate obliquely and oblique apertures can be simply produced by positioning a finger milling cutter obliquely.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Sliding Valves (AREA)
US05/771,979 1976-03-04 1977-02-25 Distributing valve on a hydraulic rotary piston engine Expired - Lifetime US4106883A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2608887A DE2608887C2 (de) 1976-03-04 1976-03-04 Steuerdrehschiebereinrichtung bei einer Rotationskolbenmaschine für Flüssigkeit
DE2608887 1976-03-04

Publications (1)

Publication Number Publication Date
US4106883A true US4106883A (en) 1978-08-15

Family

ID=5971482

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/771,979 Expired - Lifetime US4106883A (en) 1976-03-04 1977-02-25 Distributing valve on a hydraulic rotary piston engine

Country Status (6)

Country Link
US (1) US4106883A (da)
JP (1) JPS52125804A (da)
BR (1) BR7701299A (da)
DE (1) DE2608887C2 (da)
DK (1) DK143460C (da)
GB (1) GB1565414A (da)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4285643A (en) * 1978-05-08 1981-08-25 White Harvey C Rotary fluid pressure device
US4323335A (en) * 1980-02-28 1982-04-06 Danfoss A/S Distributor valve for hydraulic planetary piston machine
US4484870A (en) * 1982-01-04 1984-11-27 Zaporozhsky Konstruktorskotekhnologichesky Institut Selskokhozyaistvennoc o Mashinostroenia Planetary hydraulic motor with irregularly arranged valving parts
US4592704A (en) * 1984-03-05 1986-06-03 Eaton Corporation Motor with improved low-speed operation
US4934911A (en) * 1987-04-01 1990-06-19 Mannesmann Rexroth Gmbh Hydraulic rotary piston engine having inproved commutator valve
US5195559A (en) * 1988-09-17 1993-03-23 Werner Breitweg Rotary slide valve for auxiliary-power steering devices for motor vehicles
US6397889B1 (en) * 1998-11-18 2002-06-04 Zf Lenksysteme Gmbh Method for mounting a rotary valve for power assisted steering systems, especially for motor vehicles
EP4012184A1 (en) * 2020-12-14 2022-06-15 White Drive Motors and Steering sp. z o.o. Hydraulic machine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2907076C2 (de) * 1979-02-23 1984-07-05 Danfoss A/S, Nordborg Steuerdrehschiebereinrichtung für eine hydraulische Kreiskolbenmaschine
US4240567A (en) * 1979-05-09 1980-12-23 Nordson Corporation Pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3473437A (en) * 1966-07-19 1969-10-21 Danfoss As Rotary slide valve for fluid motors and pumps
US3516437A (en) * 1968-05-17 1970-06-23 Walter E Folkerts Valve for automobile power steering gear

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB540497A (en) * 1940-04-17 1941-10-20 Broom & Wade Ltd Improvements in and relating to compressors, blowers or the like
US3514234A (en) * 1968-06-10 1970-05-26 Char Lynn Co Fluid operated devices

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3473437A (en) * 1966-07-19 1969-10-21 Danfoss As Rotary slide valve for fluid motors and pumps
US3516437A (en) * 1968-05-17 1970-06-23 Walter E Folkerts Valve for automobile power steering gear

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4285643A (en) * 1978-05-08 1981-08-25 White Harvey C Rotary fluid pressure device
US4323335A (en) * 1980-02-28 1982-04-06 Danfoss A/S Distributor valve for hydraulic planetary piston machine
US4484870A (en) * 1982-01-04 1984-11-27 Zaporozhsky Konstruktorskotekhnologichesky Institut Selskokhozyaistvennoc o Mashinostroenia Planetary hydraulic motor with irregularly arranged valving parts
US4592704A (en) * 1984-03-05 1986-06-03 Eaton Corporation Motor with improved low-speed operation
US4934911A (en) * 1987-04-01 1990-06-19 Mannesmann Rexroth Gmbh Hydraulic rotary piston engine having inproved commutator valve
US5195559A (en) * 1988-09-17 1993-03-23 Werner Breitweg Rotary slide valve for auxiliary-power steering devices for motor vehicles
US6397889B1 (en) * 1998-11-18 2002-06-04 Zf Lenksysteme Gmbh Method for mounting a rotary valve for power assisted steering systems, especially for motor vehicles
EP4012184A1 (en) * 2020-12-14 2022-06-15 White Drive Motors and Steering sp. z o.o. Hydraulic machine
WO2022128661A1 (en) * 2020-12-14 2022-06-23 White Drive Motors And Steering Sp. Z.O.O. Hydraulic machine
US20230313818A1 (en) * 2020-12-14 2023-10-05 White Drive Motors And Steering Sp. Z.O.O. Hydraulic machine

Also Published As

Publication number Publication date
JPS5547238B2 (da) 1980-11-28
BR7701299A (pt) 1977-12-20
DK88177A (da) 1977-09-05
DK143460C (da) 1981-12-21
JPS52125804A (en) 1977-10-22
GB1565414A (en) 1980-04-23
DK143460B (da) 1981-08-24
DE2608887A1 (de) 1977-09-08
DE2608887C2 (de) 1982-09-30

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